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EP0042160A2 - Procédé et installation pour emmagasiner la chaleur et pour en élever la température - Google Patents

Procédé et installation pour emmagasiner la chaleur et pour en élever la température Download PDF

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Publication number
EP0042160A2
EP0042160A2 EP81104555A EP81104555A EP0042160A2 EP 0042160 A2 EP0042160 A2 EP 0042160A2 EP 81104555 A EP81104555 A EP 81104555A EP 81104555 A EP81104555 A EP 81104555A EP 0042160 A2 EP0042160 A2 EP 0042160A2
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EP
European Patent Office
Prior art keywords
heat
evaporator
expeller
temperature
working medium
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP81104555A
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German (de)
English (en)
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EP0042160A3 (en
EP0042160B1 (fr
Inventor
Georg Prof. Dr. Alefeld
Peter Dipl.-Phys. Maier-Laxhuber
Markus Rothmeyer
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Individual
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Individual
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Priority to AT81104555T priority Critical patent/ATE23219T1/de
Publication of EP0042160A2 publication Critical patent/EP0042160A2/fr
Publication of EP0042160A3 publication Critical patent/EP0042160A3/de
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Publication of EP0042160B1 publication Critical patent/EP0042160B1/fr
Expired legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
    • F24D11/00—Central heating systems using heat accumulated in storage masses
    • F24D11/02—Central heating systems using heat accumulated in storage masses using heat pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K17/00—Using steam or condensate extracted or exhausted from steam engine plant
    • F01K17/02—Using steam or condensate extracted or exhausted from steam engine plant for heating purposes, e.g. industrial, domestic
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B17/00—Sorption machines, plants or systems, operating intermittently, e.g. absorption or adsorption type
    • F25B17/08—Sorption machines, plants or systems, operating intermittently, e.g. absorption or adsorption type the absorbent or adsorbent being a solid, e.g. salt
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D20/00—Heat storage plants or apparatus in general; Regenerative heat-exchange apparatus not covered by groups F28D17/00 or F28D19/00
    • F28D20/003—Heat storage plants or apparatus in general; Regenerative heat-exchange apparatus not covered by groups F28D17/00 or F28D19/00 using thermochemical reactions
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
    • Y02B30/62—Absorption based systems
    • Y02B30/625—Absorption based systems combined with heat or power generation [CHP], e.g. trigeneration
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E20/00—Combustion technologies with mitigation potential
    • Y02E20/14—Combined heat and power generation [CHP]
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E60/00—Enabling technologies; Technologies with a potential or indirect contribution to GHG emissions mitigation
    • Y02E60/14—Thermal energy storage

Definitions

  • the present invention relates to a method for storing and transforming up the temperature of heat, in which a working fluid is expelled from an absorbent by heat of a predetermined medium temperature range, the working fluid vapor which is produced during the expulsion is condensed at a relatively low temperature, and the condensed working fluid in the medium temperature range evaporates and is absorbed at elevated pressure to generate absorption heat of a relatively high temperature in the absorbent.
  • the invention further relates to devices for carrying out such a method.
  • heat transformer For facilities with operating or input heat with temperatures in a medium temperature range are fed and, on the one hand, supply useful or output heat at a higher temperature level and waste heat at a lower temperature level, the term "heat transformer" has become established. This term should also be used here in the sense given.
  • the heat transformer according to DE-A-25 54 937 is intended to raise the waste heat of a power plant to a higher temperature level.
  • NH 3 is used as the working medium.
  • the heat transformer known from DE-A-26 35 557 works with the working material system NH 3 / H 2 0 / propane.
  • Heat transformers operating intermittently are also known, e.g. from DE-A-26 29 441, 27 58 727 and 28 08 464.
  • the heat transformer known from DE-A-26 29 441 is intended to generate force, with large amounts of ammonia having to be stored.
  • DE-A-27 58 727 specifies a heat transformer operated as a multi-stage store, but without specifying how the operation is to be carried out.
  • Na 2 S serves as the storage medium, which is dangerous and does not allow temperatures above 80 ° C.
  • Methylamine should be used as the working medium, which is not only toxic, but also easily decomposes.
  • CaCl 2 and LiC1 are provided as storage or absorption media. The specified facilities are very complicated and require many heat exchangers, which affects the efficiency.
  • Metal hydrides could also be used as the working material system.
  • the metal / hydrogen working substance system can only be used with a heat transformer that works according to the absorber principle, which is associated with considerable technical outlay.
  • hydrogen gas there is always a certain risk of explosion, and the swelling of the hydrides during the hydrogen uptake poses problems that are difficult to solve technically.
  • Heat transformers are needed for many purposes: heat supply and power generation are often coupled with each other, for example in thermal power stations, in diesel and gas engines that drive generators or compressor heat pumps and their. Waste heat is used in the process heat supply, for example in the chemical and food industries. On the one hand, effective heat storage is required because of the very differently structured heat and power requirements. On the other hand, the temperature level of the available heat often has to be increased in order to be able to use this heat. For example, thermal power plants are generally operated with optimal efficiency in terms of electricity generation, which means that the waste heat should be generated at the lowest possible temperature level. In contrast, the supply temperature of the heat transfer medium must be certain for the district heating supply must have increasing minimum value with increasing district heating demand.
  • a storage system that supplies heat at a level that is higher than the load level during peak loads of the district heating network (e.g. load at night with 100 ° C and heat output during peak load periods with 130 ° C to 150 ° C) would result in a significant improvement in the overall efficiency of the Thermal power plant and district heating supply.
  • heat is generated in the cooling circuit of the drive machine at 80 ° C to 100 ° C. This temperature level is too low for a district heating network or for process heat, since flow temperatures between 120 and 150 ° C are often required here.
  • a store is required that not only provides compensation for fluctuating demand, but also can deliver the heat at a higher temperature level than it has been stored.
  • Waste heat is often generated in industry, which can no longer be used because it is too low and / or is not required at the time it is generated and / or at the place where it is generated.
  • discontinuous heat transformers can be used advantageously for storage, step-up transformation of the temperature level and, if necessary, transport of heat.
  • the present invention is therefore based on the object of specifying a storage heat transformer which, in contrast to the prior art, works with environmentally friendly and harmless substances and, in contrast to the prior art, also has starting or useful heat temperatures higher than 100 ° C., in particular It is capable of delivering starting temperatures above 150 ° C to 250 ° C or even 300 ° C.
  • the invention solves this problem by a method for storing and transforming the temperature of heat, in which a working medium is expelled from an absorption medium by heat of a predetermined medium temperature range, the working medium vapor produced during the expulsion is condensed at a relatively low temperature and the condensed working medium in evaporated middle temperature range and is absorbed at elevated pressure with the generation of heat of absorption of a relatively high temperature in the absorbent, which is characterized in that a zeolite is used as the absorbent and water as the working medium.
  • the zeolite / H 2 O working substance system is therefore used in the methods and devices according to the invention.
  • This working material system is environmentally friendly and non-toxic, so that no expensive safety precautions are necessary and can also be used in publicly accessible areas.
  • this working material system used according to the invention in a heat transformer has the advantage that the desired useful heat temperatures of at least 130 ° C, in particular above 150 ° C to 250 ° C and possibly even up to 300 ° C and above can be achieved with good efficiency.
  • zeolite / H 2 o as a working material system has only been used in a cooling system (US-A-40 34 569) operated with low-temperature heat, such as solar heat, and in a small air conditioning system (US-A-41 21 432, which is equipped with an evaporator or Condenser temperatures of approximately 4 ° C or 43 ° C.
  • a cooling system US-A-40 34 569 operated with low-temperature heat, such as solar heat
  • a small air conditioning system US-A-41 21 432, which is equipped with an evaporator or Condenser temperatures of approximately 4 ° C or 43 ° C.
  • US-A-41 21 432 which is equipped with an evaporator or Condenser temperatures of approximately 4 ° C or 43 ° C.
  • given temperature and pressure ranges do not indicate that the zeolite / H 2 0 working fluid system can be used in a heat transformer for storing heat and for producing useful heat at a temperature level of up to 300 ° C. and
  • FIG. 1 schematically shows a single-stage heat transformer 100, to which input heat is supplied from a heat source 102.
  • the input heat can be in the exhaust steam from a steam turbine system, in a fluid heated by the waste heat of a gas turbine process or in the heat carrier of a flow or return line of a district heating system, a heat carrier heated by the waste heat from an engine or an industrial process, or one heated by concentrated solar heat (solar furnace) Heat transfer media should be included.
  • the input heat from the heat source 102 is fed to a heat accumulator 114 via a heat transfer circuit, which contains a heat exchanger element 112 contained in the heat accumulator 114, which for the sake of simplicity is shown as a heat exchanger coil, but in practice it can be, for example, a fin or finned heat exchanger arrangement or the like. This also applies to the other in the drawings as heat exchange suppression T shown gen and designated heat exchanger elements.
  • shut-off valves 108, 110 In the heat transfer circuit there are also two shut-off valves 108, 110 and, when using an initially vaporous heat transfer medium, such as steam, condensed in the heat exchanger coil 112, a storage vessel 107, as well as a feed pump 109, which feeds the heat transfer medium back to the heat source 102.
  • an initially vaporous heat transfer medium such as steam
  • a storage vessel 107 As well as a feed pump 109, which feeds the heat transfer medium back to the heat source 102.
  • the heat accumulator 114 contains a zeolite as a sorbent and advantageously H 2 0 as a working medium.
  • the temperature of the heat carrier in the heat exchanger coil 112 can be in the order of 100 ° C., for example between 80 and 110 ° C.
  • the heat accumulator 114 can also contain a heat exchanger coil 116, through which a heat carrier is passed in order to extract the initial or useful heat.
  • the heat exchanger coil 116 can, for example, supply heat to a district heating supply network.
  • a working medium output line 118 is connected to the heat accumulator 114, which contains a valve 120 and leads to a condenser 122, which operates at a relatively low temperature and contains a heat exchanger 124, via which the waste heat resulting from the condensation to a cooling tower, a flow or the like.
  • the condensed working medium which advantageously consists of water, then flows via a line 126, which contains a valve 128, into a storage vessel 130.
  • the storage vessel 130 is connected via a line 132, which contains a pump 134, to the inlet of an evaporator 136 , the output of which is connected to a working medium input of the heat accumulator 114 via a working medium input line 138, which contains a shut-off or check valve 140.
  • the evaporator 136 includes a heater coil 142, one. Includes input line 144 with a valve 146 and an output line 148 with a valve 150. The input line 144 and the output line 148 are connected to the parts of the lines 104 and 106 located between the heat source 102 and the valves 108 and 110, respectively.
  • the line 132 can lead through a heat exchanger 152 connected into the outlet line 148.
  • the working fluid input line 138 may include a compressor 154.
  • the pieces of lines 104 located between heat exchanger coil 112 and valves 108 and 110, respectively and 106 may be connected to a line 156 containing a valve 158 and a line 160 containing a valve 162 and a circulation pump 164, respectively.
  • the useful heat can also be removed via the heat exchanger coil 112.
  • the heat transfer circuit leading through the heat source 102 and the heat transfer circuit containing the lines 156, 160 must contain the same heat transfer medium for the removal of the useful heat.
  • valve positions, pump operating states, temperatures and pressures for the operation of the device shown in FIG. 1 when the heat accumulator 114 is loaded and discharged are given in Table 1.
  • heat at a temperature level T 1 (eg 60 to 130 ° C.) from the heat source 102 is fed into the heat accumulator 114 via the heat exchanger coil 112 by means of a heat transfer fluid, which can be liquid H 2 O, for example.
  • the heat accumulator contains a zeolite loaded with water as a storage medium in the fully or partially de-landed state. The heat supply expels water vapor from the zeolite, which flows via line 118 into condenser 122, condenses there and is collected in storage vessel 130.
  • the heat exchanger 124 can be connected in a separate circuit which contains a cooling device working with river water or ambient air and, for example, with NH 3 or a fluorocarbon such as CCl 2 F 2 or CHClF 2 or the like. works as a heat transfer medium.
  • the heat accumulator 114 When the heat accumulator 114 is discharged, that is to say when generating initial or useful heat, water is pumped into the evaporator 136 by means of the pump 134 and is evaporated there by heat from the heat source 102. The water vapor which is generated at a relatively high pressure corresponding to the temperature of the heat source 102 is absorbed in the zeolite in the heat accumulator 114. The resulting heat of absorption is conducted to the consumer via the heat exchanger coil 112 by means of the heat transfer fluid conveyed by the pump 164. If the useful heat transfer circuit works with a heat transfer fluid that is immiscible with the heat transfer fluid from the heat source 102, the useful heat is removed via the heat exchanger 116.
  • the pressure of the working fluid which has a value p 0 (for example 0.01 bar) corresponding to the condenser temperature T 0 in the storage vessel 130, is increased by the pump 134 to a value p 1 (for example 1 bar) which corresponds to the temperature T 1 of the heat source 102 corresponds, increased in the evaporator 136.
  • p 0 for example 0.01 bar
  • p 1 for example 1 bar
  • the heat exchanger 152 which is connected into the return line 148 of the heat transfer medium from the heat source 102.
  • the preheating of the working fluid fed into the evaporator 136 results in a higher average temperature and thus a higher vapor pressure in the evaporator 136, which in turn increases the temperature level of the useful heat in the store 114 and also the gassing width and thus the efficiency for the zeolite in the store 114 results.
  • the heat transfer medium in the heat exchanger coils 112 or 116 advantageously flows in the opposite direction to the heat transfer medium in the heat exchange coil 112 when the storage cylinder is loaded.
  • a further advantageous development of the device according to FIG. 1 is to provide a heat exchanger coil 166 in the reservoir 130, which is connected to the line 104 via lines 168, 170 and a three-way valve 172 and serves to drain the water in the reservoir 130 by means of a partial flow of the Heat carrier from the flow line 104 from the heat source 102 to such an extent that the temperature in the storage vessel 130 is slightly higher than in the heat exchanger coil 142. Since the valve 128 is closed when the accumulator is discharged, that is to say when generating useful heat, this is sufficient pressure build-up in the reservoir 130 to convey the water into the evaporator 136 without the aid of the pump 134, so that a control valve can then be used instead of the pump 134.
  • the heat exchanger 152 can then also be omitted. If the heat source 102 supplies steam as the heat transfer medium, the heat exchanger coil 166 will advantageously only use the superheating heat of the steam, so that the heat exchanger coil 142 is then supplied with almost saturated steam or wet steam.
  • the three-way valve 172 shuts off the line 168 during the loading process (if desired, the line 170 can also contain a shut-off valve (not shown)), while during the unloading process it is set such that a desired part of the heat transfer stream from the heat source 102 flows through the heat exchanger coil 166 .
  • the heat exchanger coil 112 For safety reasons, it may sometimes be appropriate to only charge the heat exchanger coil 112 with steam. So if the heat source 102 evaporates one Steam power plant supplies as a heat carrier, the heat exchanger coils 112 and 142 work as condensers. In this case, in order to prevent the power plant circuit from mixing with the district heating circuit, the useful heat (possibly also as steam) is better removed via the heat exchanger coil 116.
  • the exhaust gases from a gas turbine or an engine are used as heat carriers from the heat source, cooling of these exhaust gases occurs in the heat exchanger coils 112 and 142.
  • such exhaust gases can also be used to generate steam in a waste heat boiler, which then serves as a heat carrier for the input heat.
  • the evaporator 136 can then be integrated into the waste heat boiler, ie the steam generated in this way can be introduced directly into the store 114 via the valve 140 during the discharge process.
  • the accumulator 114 can be connected to a vacuum pump (not shown) via a line 174 provided with a shut-off valve.
  • the heat exchanger coil 112 or 116 In order to utilize the storage capacity as completely as possible and in particular to even out the temperature of the initial or useful heat removed from the store, it is advantageous to provide the heat exchanger coil 112 or 116 with a plurality of outlets, as is shown, for example, in FIG. 2.
  • the heat exchanger coil 112 is divided here into three sections 112a, 112b and 112c, which can be switched into the heat transfer circuit by lines with valves 176a, 176b and 176c.
  • the heat exchanger coil 116 can be divided and connected accordingly.
  • the segments of the store cooled by the connected sections 112a, 112b and 112c preferentially absorb the working fluid vapor offered by the evaporator 136.
  • First valve 176 is opened, valves 176b and 176c remain closed.
  • the water vapor is then preferably absorbed in the segment of the storage 114 which contains the section 112a and is cooled thereby.
  • valve 176a is closed and valve 176b is opened.
  • the segment of the store containing section 112a is then further discharged, but at the same time as much additional heat is withdrawn from the segment of the store containing section 112b as is necessary to achieve the desired outlet or flow temperature.
  • valve 176b is then closed and the valve 176c is opened.
  • This discharge mode is also advantageous if the storage e.g. was not fully loaded due to time constraints. Areas of different degrees of expulsion then arise when the working fluid is expelled during heat storage, which is highest at the entry point of the heat transfer medium from the heat source 102 and lowest at the exit point. By allowing the heat transfer medium to flow in the opposite direction to the loading and discharging the storage segment by segment, an optimal use of the storage can be achieved.
  • heat accumulator 114 instead of the heat accumulator 114, two or more heat accumulators of the same type can be used, which can be connected in parallel in order to adapt to the fluctuations in load in the required number or can be operated as an expeller or absorber in order to implement quasi-continuous operation of the heat transformer 100 with a phase shift.
  • the temperature level of the useful heat can first be increased by the compressor 154, which serves to increase the pressure of the working medium generated in the evaporator 136 (e.g. water vapor) and thus the temperature level of the useful heat generated during absorption.
  • a compressor can also serve to increase the gassing width and thus the utilization and the efficiency of the storage 114 at a given useful heat temperature level.
  • “Fumigation width” is understood to mean the difference in the concentration of the zeolite in absorbed working materials, such as water, in the loaded and unloaded state.
  • FIG. 3 shows a modified part of the device according to FIG. 1.
  • the same parts are provided with the same reference symbols.
  • a compression heat pump 180 is switched on to increase the pressure and temperature level in the evaporator 136 and the fumigation width of the zeolite in the storage 114.
  • the compression heat pump 180 includes an evaporator 182, which is supplied with heat by the heat transfer medium from the heat source 102.
  • the evaporated working fluid of the compression heat pump is operated by a compressor 185 compresses and condenses in the heating coil 142 of the evaporator 136, which also works as a condenser of the compressor heat pump.
  • the condensed working medium is conveyed back to the evaporator 182 by a throttle valve 184.
  • the evaporation temperature in the evaporator 136 and the expulsion temperature in the storage 114 can also be increased by connecting the heat source 102 to a compressor heat pump, in which case the condenser heat of this compressor heat pump both the evaporator 136 and the heating or heat exchanger coil 112 with a higher value Heat operated (not shown).
  • the continuously operating heat transformer 100 is connected upstream of the continuously operating heat transformer 100.
  • This contains an expeller 214 a, a condenser 222, a pump 234, an evaporator 236 and an absorber 214b.
  • An absorbent circuit 286 is also provided, which contains an expansion device 288 and a pump 290.
  • the heat transformer 200 is a known device and is only shown schematically, for example the usual heat exchangers such as that between poor and rich solution in the absorption medium circuit are missing.
  • the absorption heat is removed from the absorber 214b via a heat exchanger coil 216 and via a heat transfer circuit which contains a line 204, a heat exchanger 292 connected therein for the removal of useful heat, the heating coil 112 for the storage 114, a storage vessel 207 and a pump 209. Otherwise, the components of the discontinuously operating heat transformer are the same Reference numerals as in Fig. 1 provided.
  • heat Q (T 1 ) from heat source 102 (not shown in FIG. 4) is fed into expeller 214a and evaporator 236. Waste heat Q (T O ) at the temperature level T O is dissipated to the environment from the condenser 222. Useful heat Q (T 2 ) is generated in the absorber 214b at the temperature level T 2 . The heat Q (T 2 ) is withdrawn via the heat exchanger coil 216 and fed into the memory 114 via the heat exchanger coil 112, as has been explained with reference to FIG. 1. If desired, useful heat with the temperature level T 2 can also be removed from the heat exchanger 292 via a heat exchanger coil 294.
  • the waste heat generated in the condenser 122 and the waste heat generated in the condenser 222 can be dissipated to the environment via a common cooling tower or a common flow cooling device or the like.
  • the absorption of the expelled working substance in the storage 114 and the removal of the useful heat generated thereby are carried out, as has been described with reference to FIG. 1.
  • the heat of vaporization for the evaporator 136 is taken from the heat source (102 in FIG. 1) not shown in FIG. 4. Overall, this results in a temperature level T 3 which is higher than T 2 for the useful heat removed, for example, via the heat exchanger coil 116.
  • the theoretical efficiency of the device as a whole is approximately 1/3, ie approximately one third of the total amount of heat that is supplied to the devices 214a, 236 and 136 at the temperature level T 1 can be extracted as useful heat at the temperature level T 3 .
  • a further increase in the temperature level T 3 of the useful heat that can be taken from the storage 114 can be achieved in that the evaporator 136 is not supplied with heat from Q (T 1 ) of the temperature T 1 from the heat source 102, but with heat Q (T 2 ) from absorber 214b.
  • the device according to FIG. 4 can be modified as shown in FIG. 5.
  • the heat transformer 100 on the right side of FIG. 5 is only shown in part and is otherwise designed in accordance with FIG. 1.
  • the heat transfer medium from the heat exchanger coil 216 is thus conducted via the lines 144 and 148 through the heating coil 142 of the evaporator 136, as was explained with reference to FIG. 1.
  • 5 increases the temperature level T 3 of the useful heat Q (T 3 ) which can be taken from the storage 114, but the theoretical efficiency is reduced to about 1/4.
  • the heat exchanger coil 294 and the heat exchanger coil 116 can be connected in series, which is advantageous if the useful heat is used to remove a liquid heat transfer medium such as water from a temperature below T 2 to heat to the temperature T 3 (starting temperature of the heat accumulator 114).
  • the evaporator 136 (FIGS. 1 and 5) of the discontinuously operating heat pump of the heat transformer 100 can be placed in the absorber 214 b (FIG. 4) of the continuously operating one warmth Integrate the heat transformer 200 pump.
  • FIG. 6 the discontinuously operating heat transformer, which corresponds to the heat transformer 100 in FIGS. 1 and 5, with 300 and the continuously working heat transformer with 400. Parts of the same function are designated by the same reference numerals in FIGS. 1, 5 and 6.
  • the output side of the heat exchanger coil 216 is connected via a valve 611 to a line 204 which contains a further valve 613 and leads to the input side of the heating or heat exchanger coil 112 of the store 114. Between the valves 611 and 613 branches off the working fluid inlet line 138 containing the valve 140 (and, if desired, the compressor 154).
  • the outlet side of the valve 128 is connected to a first storage vessel, the outlet of which is connected via a valve 615 and a line 617 to a second storage vessel 130b, into which the outlet line 106 of the heat exchanger coil 112 also opens.
  • the heat exchanger 292 is connected with an input side via a valve 619 to the output side of the heat exchanger coil 216 and with its output side. connected to line 617.
  • the heat generated in the absorber 214b of the continuous heat transformer 400 is used, on the one hand, via the heat exchanger coil 112 to expel the water vapor from the zeolite contained in the storage 114 and also to generate water vapor for absorption and production of useful heat in the storage 114.
  • the valve positions and temperatures of the various units 6 are listed in Table 2.
  • the heat exchanger 292 enables this Extraction of useful heat at the temperature level of the absorber 214b.
  • the outgassing pressure can be selected so that the waste heat in the condenser 122 arises at such a high temperature level that this heat is still suitable for feeding into the evaporator 236 and / or the expeller 214a, which results in a theoretical power factor of 1/3 .
  • both heat from the condenser 122 at the temperature level T 1 ′ and heat from the heat source 102 at the temperature level T 1 are fed into the evaporator 236 and / or the expeller 214a.
  • Useful heat at the temperature level of the absorber 214b can be taken from the heat exchanger 292 via the heat exchanger coil 294; the heat exchanger coil 294 can also be connected upstream of the heat exchanger coil 116.
  • the valve 615 is necessary because the reservoir 130b is at a higher pressure than the condensate from the condenser 122 in the reservoir 130a during the expulsion.
  • the continuous heat transformer 200 and 400 are in operation both during the drive-out cycle and during the absorption cycle of the store 114.
  • FIG. 7 shows a device which contains a combination of a discontinuously operating heat transformer with an upstream, likewise discontinuously operating heat transformer. the condenser 124 and the evaporator 136 being common to both heat transformers.
  • the device according to FIG. 7 contains two series-connected, discontinuously operating heat transformers of the type explained with reference to FIG. 1, and the same reference numbers as in FIG. 1 were therefore also used.
  • the same reference numbers as in FIG. 1 were therefore also used.
  • one or two dashes are added to the relevant reference symbols. The same applies to components that are required for each of the two heat transformers.
  • valves are designated which enable the loading or unloading of the stores 114 'or 114 "explained in sections with reference to FIG. 2.
  • the memory 114 ' is charged by heat of the temperature T 1 from the heat source 102 via the heat exchanger coil 112'.
  • Working vapor is then generated by evaporation in the evaporator 136 by means of heat from the heat source 102, with which the heat accumulator 114 ′ is discharged.
  • the heat generated when the working medium is sorbed in the absorbent in the storage 114 ' is coupled out via the heat exchanger coil 116' and fed to the heat exchanger coil 112 "of the storage 114", where the heat is used to expel the working medium from the absorbent contained in the heat accumulator 114 ".
  • the heat for the evaporator 136 is removed by a heat transfer circuit which contains the heat exchanger coil 112 'and the pump 134 ".
  • an additional valve 101 is provided in line 104
  • the pressure in the evaporator 136 and thus the useful heat level in the absorption in the heat store 114 ′′ are increased further, but at the expense of the efficiency.
  • Zeolites of types A, X and Y have proven to be particularly suitable.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • General Chemical & Material Sciences (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • Sorption Type Refrigeration Machines (AREA)
  • Gas Or Oil Filled Cable Accessories (AREA)
  • Battery Electrode And Active Subsutance (AREA)
  • Central Heating Systems (AREA)
EP81104555A 1980-06-13 1981-06-12 Procédé et installation pour emmagasiner la chaleur et pour en élever la température Expired EP0042160B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT81104555T ATE23219T1 (de) 1980-06-13 1981-06-12 Verfahren und einrichtung zum speichern und hochtransformieren der temperatur von waerme.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3022284 1980-06-13
DE19803022284 DE3022284A1 (de) 1980-06-13 1980-06-13 Verfahren und einrichtung zum speichern und hochtransformieren der temperatur von waerme

Publications (3)

Publication Number Publication Date
EP0042160A2 true EP0042160A2 (fr) 1981-12-23
EP0042160A3 EP0042160A3 (en) 1982-03-03
EP0042160B1 EP0042160B1 (fr) 1986-10-29

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ID=6104588

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EP81104555A Expired EP0042160B1 (fr) 1980-06-13 1981-06-12 Procédé et installation pour emmagasiner la chaleur et pour en élever la température

Country Status (5)

Country Link
US (1) US4410028A (fr)
EP (1) EP0042160B1 (fr)
JP (1) JPS5726392A (fr)
AT (1) ATE23219T1 (fr)
DE (2) DE3022284A1 (fr)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2642509A1 (fr) * 1989-01-11 1990-08-03 Elf Aquitaine Dispositif pour la production du froid et/ou de la chaleur par reaction solide-gaz
DE3909697A1 (de) * 1989-03-23 1990-09-27 Siemens Ag Rauchgas-reinigungssystem
GB2438065A (en) * 2006-05-08 2007-11-14 Lear Corp Connector for airflow between an air conditioning device and a plenum member in a vehicle seat
DE102007039657A1 (de) * 2007-08-22 2009-02-26 Behr Gmbh & Co. Kg Vorrichtung zum Heizen und/oder Klimatisieren und Anordnung einer Vorrichtung zum Heizen und/oder Klimatisieren in einem Kraftfahrzeug
AT512138A1 (de) * 2011-05-27 2013-05-15 Vaillant Group Austria Gmbh Anlage zur Kraft-Wärmekopplung mit kombinierten Wärmespeichern
WO2019115252A1 (fr) * 2017-12-15 2019-06-20 IFP Energies Nouvelles Stockage et restitution d'energie thermique pour chauffage urbain par adsorption et desorption sur moyens de stockage thermochimique de type zeolithique

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DE3207656A1 (de) * 1982-02-15 1983-08-25 Hieronimi, Ulrich, 8000 München Sorptionsapparate und verfahren fuer ihren betrieb
CA1212284A (fr) * 1982-08-23 1986-10-07 Mitsuyoshi Miura Appareil chauffant
US4519441A (en) * 1982-09-30 1985-05-28 Spevack Jerome S Heat conversion system
DE3408192C2 (de) * 1984-03-06 1987-03-26 Markus 8058 Erding Rothmeyer Verfahren zum Hochtransformieren der Temperatur von Wärme sowie Wärmetransformator
US4594856A (en) * 1985-03-04 1986-06-17 Markus Rothmeyer Method and device for pumping heat
DE3509564A1 (de) * 1985-03-16 1986-09-18 Thomas Dipl.-Ing. 7500 Karlsruhe Föllinger Apparatur zur durchfuehrung von adsorption, desorption und innerem waermeaustausch
FR2590356B1 (fr) * 1985-11-19 1989-06-02 Jeumont Schneider Dispositif pour la production en continu de chaud et de froid
JPS6332263A (ja) * 1986-07-25 1988-02-10 ダイキン工業株式会社 水素吸蔵合金を利用する補助加熱装置
ES2036677T3 (es) * 1987-04-14 1993-06-01 Uwe Rockenfeller Sistema de acumulacion de energia quimica.
US5241831A (en) * 1989-11-14 1993-09-07 Rocky Research Continuous constant pressure system for staging solid-vapor compounds
US5263330A (en) * 1989-07-07 1993-11-23 Rocky Research Discrete constant pressure system for staging solid-vapor compounds
US5535817A (en) * 1989-07-28 1996-07-16 Uop Sorption cooling process and apparatus
US5503222A (en) * 1989-07-28 1996-04-02 Uop Carousel heat exchanger for sorption cooling process
US5456093A (en) * 1989-07-28 1995-10-10 Uop Adsorbent composites for sorption cooling process and apparatus
DE10115090B4 (de) * 2001-03-27 2006-07-06 Luther, Gerhard, Dr.rer.nat. Wärmepumpen gestützte zeitversetzte Nutzung von Niedertemperaturwärme zu Heizzwecken
GB2422652B (en) * 2005-01-26 2009-09-23 Danisco Process for producing steam and a steam compressor
DE102007022950A1 (de) * 2007-05-16 2008-11-20 Weiss, Dieter Verfahren zum Transport von Wärmeenergie und Vorrichtungen zur Durchführung eines solchen Verfahrens
WO2009000029A1 (fr) * 2007-06-22 2008-12-31 Commonwealth Scientific And Industrial Research Organisation Système pour augmenter une chaleur résiduelle
US20110146939A1 (en) * 2008-06-16 2011-06-23 Carbon Zero Limited Energy absorption and release devices and systems
CA2862079C (fr) * 2012-01-23 2017-01-03 Siemens Aktiengesellschaft Centrale thermique en montage-bloc et procede pour la faire fonctionner
RU2609266C2 (ru) * 2015-01-21 2017-01-31 Алексей Сергеевич Маленков Система теплохладоснабжения
CN109184831B (zh) * 2018-10-17 2023-10-20 中国船舶重工集团公司第七0三研究所 一种供能侧可多能切换、解耦型热储能多能供应系统
US20240151411A1 (en) * 2022-11-04 2024-05-09 Jayvic, Inc. Thermal Liquid Battery

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US4034569A (en) * 1974-11-04 1977-07-12 Tchernev Dimiter I Sorption system for low-grade (solar) heat utilization
GB1572737A (en) * 1977-01-17 1980-08-06 Exxon France Heat pump
DE2808464A1 (de) * 1977-03-01 1978-09-21 Pro Elektra Ag Baden Verfahren und anordnung zur periodischen speicherung und freigabe von waerme
US4138861A (en) * 1977-03-24 1979-02-13 Institute Of Gas Technology, A Nonprofit Corporation Solid adsorption air conditioning apparatus and method
US4121432A (en) * 1977-03-24 1978-10-24 Institute Of Gas Technology Solid adsorption air conditioning apparatus and method
SE7706357A0 (sv) * 1977-05-31 1978-12-01 Ray Olsson Sätt vid kylning av ett utrymme samt anordning för genomförande av sättet
DE2810360A1 (de) * 1978-03-10 1979-10-04 Dieter Brodalla Chemische waermespeicherpumpe
EP0008929A1 (fr) * 1978-09-05 1980-03-19 John Walter Rilett Moteurs et leur dispositif d'alimentation en gaz
GB2029908A (en) * 1978-09-05 1980-03-26 Rilett J W Motors and gas supply apparatus therefor
FR2441134A1 (fr) * 1978-11-10 1980-06-06 Anvar Nouveau capteur solaire a deux compartiments pour la refrigeration et la recuperation de calories
DE2939423A1 (de) * 1979-09-28 1981-04-16 Alefeld, Georg, Prof.Dr., 8000 München Verfahren zum betrieb einer eine absorber-waermepumpe enthaltenden heizungsanlage und heizungsanlage zur durchfuehrung dieses verfahrens
US4321799A (en) * 1980-03-28 1982-03-30 Georgia Tech Research Institute Method for utilizing gas-solid dispersions in thermodynamic cycles for power generation and refrigeration

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2642509A1 (fr) * 1989-01-11 1990-08-03 Elf Aquitaine Dispositif pour la production du froid et/ou de la chaleur par reaction solide-gaz
EP0382586A1 (fr) * 1989-01-11 1990-08-16 Societe Nationale Elf Aquitaine Dispositif pour la production du froid et/ou de la chaleur par réaction solide-gaz
DE3909697A1 (de) * 1989-03-23 1990-09-27 Siemens Ag Rauchgas-reinigungssystem
GB2438065A (en) * 2006-05-08 2007-11-14 Lear Corp Connector for airflow between an air conditioning device and a plenum member in a vehicle seat
GB2438065B (en) * 2006-05-08 2008-11-12 Lear Corp Air routing system and method for use with a vehicle seat
US7607739B2 (en) 2006-05-08 2009-10-27 Lear Corporation Air routing system and method for use with a vehicle seat
DE102007039657A1 (de) * 2007-08-22 2009-02-26 Behr Gmbh & Co. Kg Vorrichtung zum Heizen und/oder Klimatisieren und Anordnung einer Vorrichtung zum Heizen und/oder Klimatisieren in einem Kraftfahrzeug
AT512138A1 (de) * 2011-05-27 2013-05-15 Vaillant Group Austria Gmbh Anlage zur Kraft-Wärmekopplung mit kombinierten Wärmespeichern
AT512138B1 (de) * 2011-05-27 2014-02-15 Vaillant Group Austria Gmbh Anlage zur Kraft-Wärmekopplung mit kombinierten Wärmespeichern
WO2019115252A1 (fr) * 2017-12-15 2019-06-20 IFP Energies Nouvelles Stockage et restitution d'energie thermique pour chauffage urbain par adsorption et desorption sur moyens de stockage thermochimique de type zeolithique
FR3075320A1 (fr) * 2017-12-15 2019-06-21 IFP Energies Nouvelles Stockage et restitution d'energie thermique pour chauffage urbain par adsorption et desorption sur moyens de stockage thermochimique de type zeolithique

Also Published As

Publication number Publication date
EP0042160A3 (en) 1982-03-03
DE3175535D1 (en) 1986-12-04
JPS5726392A (en) 1982-02-12
ATE23219T1 (de) 1986-11-15
DE3022284A1 (de) 1982-01-14
US4410028A (en) 1983-10-18
EP0042160B1 (fr) 1986-10-29

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